Oscillating shear for cutting trapezoidal shapes



Oct. 23, 1956 s. BUDLONG ETAL 2,767,789

OSCILLATING SHEAR FOR CUTTING TRAPEZOIDAL SHAPES Filed June 1; 1954 a Sheets-Sheet 1 Oct. 23, 1956 s. BUDLONG ET AL 2,767,789

OSCILLATING SHEAR FOR CUTTING TRAPEZOIDAL SHAPES Filed June 1. 1954 8 Sheets-Sheet 2 J23 JZZ l J25 J26 J32 HUI MIM Oct. 23, 1956 s. BUDLONG ET AL OSCILLATING SHEAR FOR CUTTING TRAPEZOIDAL SHAPES 8 Sheets-Sheet 3 Filed June 1. 1954.

Oct. 23, 1956 s. BUDLONG ET AL OSCILLATING SHEAR FOR CUTTING TRAPEZOIDAL SHAPES 8 Sheets-Sheet 5 Filed June 1,1954

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Oct. 23, 1956 s. BUDLONG ET AL 2,767,789

OSCILLATING SHEAR FOR CUTTING TRAPEZOIDAL SHAPES Filed June 1, 1954 8 Sheets-Sheet 6 [WWW Oct. 23, 1956 s. BUDLONG ETAL 2,767,789

OSCILLATING SHEAR FOR CUTTING TRAPEZOIDAL SHAPES Filed June l, 1954 8 Sheets-Sheet 7 Get. 23, 1956 s. BUDLONG ET AL 2,767,789

OSCILLATING SHEAR FOR CUTTING TRAPEZOIDAL SHAPES Filed June 1. -l954 8 Sheets-Sheet 8 I J l w J@ J55 Illllllil'lll'l United States Patent OSCILLATING SHEAR FOR CUTTING TRAPEZOIDAL SHAPES Simeon Budlong and Frederick M. Littell, Chicago, Ill., assignors to F. J. Littell Machine Company, Chicago, Ill., a corporation of Illinois Application June 1, 1954, Serial No. 433,384

8 Claims. (Cl. 164-49) The invention relates to shearing mechanism of the oscillating type and has reference in particular to im- .proved mechanism for oscillating a conventional type shear between cutting operations thereof whereby to cut metal blanks of various shapes including trapezoids, parallelograms, squares and triangles.

An object of the invention resides in the provision of oscillating mechanism for a conventional type shear and which mechanism will be hydraulically actuated by means of power cylinders disposed on respective sides of the pivot axis of the shear, each power cylinder being operative to rotate the shear in one direction and wherein the power cylinders are independently adjustable in a manner to vary the extent of rotation of the shear upon operation of the cylinders respectively.

Another object is to provide new and improved mechanism for oscillating a conventional metal cutting shear which for the purpose is supported by rollers for rotary movement about a vertical axis disposed centrally of the shear, and wherein a pair of hydraulic cylinders are employed as the power means for oscillating the shear.

A more specific object of the invention is to provide oscillating shear mechanism wherein the frame together with the cutting knives of the shear are roller supported for bodily rotary movement on a hardened steel arcuate track; wherein the said frame together with the cutting knives of the shear are bodily oscillated in a horizontal plane by a pair of hydraulic power cylinders, with the' pressure fluid being alternately supplied to and exhausted from the cylinders respectively; and wherein novel means are employed for manually and independently adjusting the position of each power cylinder with respect to the piston thereof, whereby to vary the extent of oscillating movement imparted to the frame in the particular direction for that cylinder.

A further object in connection with oscillating shear mechanism resides in the provision of manually adjustable V means for varying the relative position of the power' cylinders with respect to their piston, and which said means will incorporate a universal joint intermediate the length of the actuating shaft thereof to facilitate the adjustment of novel pivot means which in turn control the, position of the power cylinders articulatedly connected thereto.

Another object is to provide hydraulic power cylinders for effecting oscillating movement of shear mechanism of any conventional type whereby to cut metal blanks of keystone shape, parallelogram shape, or blanks in the shape of a square or triangle, and wherein said power cylinders in addition to being adjustable for varying the angle of out can be employed to lock the shear in any position between its two extreme positions, preventing oscillating movement thereof. 7

Another object is to provide oscillating shear mechanism as above described which will be sturdy in construction and efiicient in operation, wherein the frame and cutting knives of the shear can be oscillated in a manner to effect a quick start, a cushioned stop, and wherein the 2,767,789 Patented Oct. 23, 1955 same is capable of infinite adjustment for movement in a clockwise and counterclockwise direction within the range of movement for the particularly machine.

With these and various other objects in view, the invention may consist of certain novel features of construction and operation as will be more fully described and particularly pointed out in the specification, drawings and claims appended hereto.

in the drawings which illustrate an embodiment of the invention and wherein like reference characters are used to designate like parts Figure 1 is a side elevational view showing the oscillating shear mechanism of the invention in combination with a feeding and straightening machine for feeding stock material thereto;

Figure 2 is a front elevational view of the oscillating shear mechanism of the invention, with parts of the base being shown in section to better illustrate certain constructional details;

Figure 3 is a horizontal sectional view taken substantially along line 33 of Figure 2 illustrating the construction and arrangement of the hydraulically powered cylinders for oscillating the shear and also the manual means for adjusting the oscillating stroke of said cylinders;

Figure 4 is a fragmentary, horizontal, sectional view similar to Figure 3 but showing the hydraulically powered cylinders in position for effecting oscillating movement of the shear from a zero center position to a 15 degree angularly displaced position on one side of the center;

Figure 5 is a fragmentary, horizontal, sectional view similar to Figure 3 but showing the hydraulically powered cylinders in position for effecting oscillating movement of the shear to and from an angularly displaced 15 degree position on the respective sides of the center;

Figure 6 is a fragmentary, horizontal, sectional View similar to Figure 3 but showing the hydrauiically powered cylinders in position for eife'cting oscillating movement of the shear 'to and from an angularly displaced 30 degree position on the respective sides of the center;

Figure 7 is a vertical, sectional view taken substantially along line 7-7 of Figure 3 and illustrating the jcurnalling structure for the pivot arms, the threaded connection of the threaded adjusting shafts therewith, and the articulated connection which the power cylinders have with the said arms;

Figure 8 illustrates various shapes as regards the metal blank which the present oscillating shear mechanism is capable of producing;

Figure 9 is a front, elevational view of the roller mechanism which supports the frame of the oscillating shear for rolling movement on an arcuate track;

Figure 10 is a schematic flow diagram of the hydraulic system for the oscillating shear mechanism of the invention, the cylinders being illustrated in a maximum adjusted position with respect to the pistons thereof; and

Figure 11 is a schematic flow diagram similar to Figure 10 but illustrating the parts in an oppositely disposed position.

Referring to the drawings, and particularly Figures 1 and 2, the oscillating shear structure of the invention has been disclosed in combination with a feeding and straightening machine identified by numeral 26, which receives metal stock material 21 from a coil or other source of supply and after passing the same through a series of rollers in order to straighten the stock, the same is fed by a pair of pinch rollers or feeding rollers to conventional shear mechanism 22 for cutting the metal stock into blanks, the shape of which may vary, depending on the ultimate use of the metal blank. In accordance with the invention, the shear mechanism 22 is provided with roller structures 23 which support the mechanism on a base such as 24, with provision being made for oscillating movement of the shear mechanism with respect to the central stud 25, which provides a vertical axis having location substantially centrally of the mechanism. Accordingly, by oscillating the shear mechanism 22, first in a clockwise and then a counterclockwise direction, with the cutting operations taking place between oscillations, a variety of shapes can be produced, the most important of which are shown in Figure 8.

The keystone shaped blank 26 is formed by oscillating the shear mechanism 22 in a clockwise direction approximately degrees from the transverse center and effecting a cutting operation of the cutting knives 27 and 28, to form the cut edge 30. The shear mechanism is then oscillated in a counterclockwise direction for approximately 30 degrees beyond the transverse center and then effecting a second operation of the cutting knives 27 and 28 to form the cut edge 31. The blank 32 of trapezoidal shape also requires clockwise and counterclockwise movement of the shear mechanism to form the cut edges 33 and 34, the mechanism being angularly displaced approximately 15 degrees from the transverse center to form the cut edge 33 with the angular displacement of the shear mechanism being somewhat less to form the cut edge 34. To form the blank 35 of trapezoidal shape the shear mechanism is oscillated in a clockwise direction approximately 15 degrees to form the cut edge 36 and then is returned to a transverse center position to form the cut edge 37. The parallelogram 38 is formed by oscillating the shear mechanism clockwise to an angularly displaced position of approximately 15 degrees and locking the shear in such position and then effecting feeding and cutting operations to form the parallel cut edges 40 and 41. By obvious variations of the previously described operations it is possible to cut metal blanks in the shape of an isosceles triangle such as 42, or in the shape of a right angle triangle such as 43. A square blank such as 44 can also be cut by the present shear mechanism, which, however, does not require oscillating movement of the shear mechanism, but, on the contrary, the mechanism is locked in position on the transverse center and the cut edges thus formed, such as 45 and 46, are normal to the pre-formed side edges of the stock material.

Referring again to Figure 1, the feeding and straightening machine consists of a supporting base which supports the frame 51 journalling the upper straightening rollers 52, the lower straightening rollers 53, and the feeding rollers 54 and 55. The shafts of the lower straightening rollers 53 and the shafts of the feeding rollers 54 and 55 are each provided with gear wheels such as 56 and which are operatively connected by means of idler gears 57 whereby the entire set of rollers are simultaneously rotated for the purpose of straightening the stock material 21 and for feeding said material in a left hand direction to the cutting knives 27 and 28 of the shear mechanism. The upper straightening rollers 52 are mounted for bodily movement in a vertical guide structure by means of the blocks 58 and said blocks and thus rollers 52 can be adjustably positioned for varying the degree of straightening action effected by the rollers. Also the upper feed roller 54 is tensioned by the coil spring 59 in the direction of the lower feed roller 55 and, accordingly, the gripping action of the feed rollers on the stock material 21 is variable as the tension of the spring 59 may be varied. For initially feeding the stock material material through the feeding rollers the upper feeding roller 54 can be cammed out of friction contact with roller 55, for which purpose there is provided the manually operable handle 60.

The stock material 21 is first presented to the rear table or extension 61 of the shear mechanism, said table being positioned in substantially horizontal alignment with the cutting edge of lower knife 28. The upper knife 27 of the shear mechanism constitutes the movable element of the cutting instrumentalities, all of which is conventional structure and need not be further described in detail.

The present invention contemplates that oscillating movement will be imparted to the shear mechanism and accordingly it is necessary for said purposes to support the shear mechanism on base 24 for rotation about the central axis 25. The base is preferably made up of welded parts which include transverse members such as 62 and longitudinal members such as 63. The top surface of the base is generally formed by member 64 and to said member are suitably fixed the arcuate track sections 65 and 66 which may be formed of hardened steel so as to present the best wearing surface for the rollers 67 constituting the main element of the roller structures 23.

Each foot structure, such as 68 of the shear mechanism, is provided with a pair of roller structures such as 23, Figure 9, each including a frame providing the spaced depending ears 70 and 71 and the connecting frame piece 72. The depending ears accommodate a shaft such as 73 on which the tapered roller 67 is journalled, the same being mounted for substantially frictionless rotation by the roller bearing assembly 74. The shaft 73 is releasably held in place by means of the threaded nut 75 and said shaft at its opposite end is provided with a lubrieating fitting 76 by means of which grease or oil may be periodically supplied to the roller bearing structure 74. Since the rollers 67 must roll in an are about the center of rotation 25, the shaft 73 is disposed at a slight inclination below the horizontal approximately two or three degrees, as best shown in Figure 9. The structure allows full rolling movement of rollers 67 on the arcuate track sections 65 and 66. In other words, the inclination of their journalling shafts prevents sliding action of the roll ers on the tracks 65 and 66 which if allowed to take place would result in excessive wear, requiring frequent replace ment.

The bed plate 78 of the shear mechanism, as best shown in Figure 2, has suitably welded thereto an adapter plate 80, the said adapter plate at its respective ends bcing provided with socket portions such as 81. The numeral 82 indicates a bolster having a length approximately equal to that of adapter plate 80 and to which is secured at each end a pin 83, see Figures 4, 5 and 6. The pins at the respective ends of bolster 82 are received in the socket openings provided by portions 81, and in this manner the bolster 82 and the shear mechanism are releasably connected so that any oscillating movement imparted to the bolster will be directly transmitted to the shear mechanism to cause similar oscillating movement thereof, and wherein rollers 67 will have rolling movement as described on their respective tracks 65 and 66. The bolster 82 is mounted for oscillating movement on a vertical axis provided by the center stud 25 suitably supported by the base 24. The stud extends upwardly into the cylindrical portion 84, constituting part of bolster 82, and by means of conventional roller bearings the bolster is supported for free rotation on the fixed center stud 25. The bolster structure is completed by the cross arm generally indicated by numeral 85, the same being formed integral therewith and which extends on respective sides of the vertical center to provide the cross arm extensions 86 and 87.

Hydraulic cylinders are employed as power means for oscillating the bolster structure and for thus in turn oscillating the shear mechanism having direct connecti n therewith. As best shown in Figures 4. 5 and 6. the hydraulic cylinders 90 and 91 each consist of a cylinder 92 and 93. respectively, and a piston identifiied hv numerals 94 and 95. respectively. The rear end of each cylinder is closed by means of a bifurcated closure member 96 and 97, respectively, which is in turn pivotally secured to pivot arms 98 and 100. The pistons 94 and of the respective power cylinders are suitably secur d to piston rods 101 and 102, which in turn are pivotally connected at 103 and 104 to the cross arm extensions 86 and 87, respectively. Pressure fluid is supplied to the cylinders alternately and it will be understood that application of the pressure fluid to a cylinder will force the piston of the cylinder in a direction toward the right to effect oscillation of the shear mechanism in either a clockwise or counterclockwise direction.

The pivot arms '98 and 100 are pivotally secured to the top plate 64 of the base 24 by means of the pins 105 and 106. At their lower ends the pins extend through a pair of overlapping plates 107 which are welded together and are in turn welded to the top plate 64. The ends of the pins 105 and 106 project below plates 107 and have threaded engagement with a plate 108 common to both pins. A wear plate such as 109 and 110 is interposed between each pivot arm and the top surface 64 of the base and said plates are suitably secured in position by screws 111 which additionally serve to fasten the thrust members 112 in position.

The pivot arms 98 and 100 have a unique formation at their outer end by means of which the arms can be pivotally connected to the cylinders and which additionally provides for adjustment of the position of'the arms for varying the piston stroke so that the extent of oscillation of the shear mechanism can be varied. As best shown in Figure 7, the outer end of each arm is bifurcated as at 113 for receiving the bifurcated end of a cylinder closure member such as 96 or 97. Pivot pins 114 are employed for fastening the bifurcated members 96 or 97 to their respective pivot arms. Also each pivot arm is recessed as at 115 for receiving the cylindrical nut 116 associated with arm 98 and the cylinder nut 117 associated with arm 100. Each cylinder nut is suitably fixed to its respective pivot arm and for adjusting purposes each cylinder nut has threaded engagement with the threaded end of an adjusting shaft, respectively, identified by numerals 118 and 119. Shaft 118 has threaded relation with cylinder nut 116 and said shaft at its right hand end is journalled in bracket 120, there being fixed to said end of the shaft the gear wheel 121. The adjusting shaft 119 has threaded relation with the cylinder nut 117 and said shaft also extends to the right and which end is journalled in bracket 122, the same having location relatively adjacent the gear wheel 123. It will be understood that the brackets 120 and 122 are each pivotally connected to a fixed support such as 126 by means of the pivot pins 124 and 125. The'pivot connection thus provided allows movement of the shafts 118 and 119 with respect to their pivot as an axis of rotation which is of course necessary as the pivot arms 98 and 100 are adjustably positioned. In other words, the cylinder nuts have movement in an arc and since said nuts carry the threaded ends of the adjusting shafts, it is necessary that the said shafts have such freedom of movement, and which is thus provided for in the present structure by pivotally supporting the right hand end of said adjusting shafts through the instrumentality of the pins 124 and 125. Each bracket, namely, 120 or 122, is provided with a depending portion 128 which journals the shaft of a universal joint 130. The shaft of said universal joint has fixed thereto the pinion 131, which meshes with its respective gear wheel either 121 or 123. The other end of the universal joint 130 is fixed to a shaft 132 and each shaft extends in a right hand direction to the front of the machine where the shafts are journalled by an indexing box 133 and have fixed to the extending end a hand wheel 134 and 135, respectively. The pointer 136, which receives movement upon rotation of the hand wheel is associated with a calibrated index plate 137 provided by index box 133 so as to indicate to the operator the degree of oscillation of the shear mechanism for any particular adjusted position of the pivot arms 98 or 100.

As shown in Figure 3, the manually actuated adjusting mechanism has effected a locked up position of the shear mechanism with the cutting blades thereof being disposed on the transverse center of the oscillating shear device as indicated by the dotted line 139 and wherein both pointers will be positioned at zero on their indexing plate 137. With the shear mechanism located in such position the same will be operative to produce square or rectangular blanks such as 44, Figure 8, the cutting blades being actuated between feeding operations to prov duce the cut edges 45 and 46. The locked up position of Figure 3 is obtained by rotating both hand wheels 134 and 135 to so locate the pivot arms 98 and 100 as to force the rear of each cylinder 92 and 93 into contact with its respective piston 94 and 95. In other words, each cylinder of the hydraulic power means is caused to telescope its piston to the maximum extent, effecting contact of each piston with the rear end of its cylinder. As a result the cross arm is located at right angles with respect to the transverse center so that the dotted line 140, which bisects the cross arm, indicates the direction of feed of the stock material. With pivot arms 98 and 100 in the position as shown in Figure 3, it will be observed that the thrust plates 112 have been fastened to the base in a position whereby said thrust plates have substantially full contact with the thrust flange 141 provided for the purpose on the outer edge of each pivot arm, as shown in Figure 7.

In Figure 4 the power cylinder 91 has been adjusted to provide for substantially 15 degree oscillation of the shear mechanism from a transverse center position. No adjustment is made as to the pivot arm 93 and by maintaining the said position of this pivot arm and power cylinder oscillation of the shear mechanism will be caused to take place to and from the transverse center. Thus, hand wheel 135 is actuated to cause rotation of shaft 132 thereof and through pinion 131 the gear 123 will be rotated to in turn rotate adjusting shaft 119. The shaft is rotated in that direction to cause rearward movement of the pivot arm 100 until the desired position is reached as indicated by the pointer 136 of hand wheel 135. As a result the cylinder 93 is displaced rearwardly with respect to its piston and upon supplying pressure fluid alternately to the hydraulic cylinders corresponding oscillating movement will be imparted to'the shear mechanism.

In Figure 5 the pivot arms 98 and have been so adjusted as to provide for approximately 15 degree oscillating movement of the shear mechanism on both sides of the transverse center. To secure such operation it is necessary to adjust pivot arm 98 similar to the adjustment of pivot arm 100 as described in connection with Figure 4. The hand Wheel 134 is accordingly rotated to rotate adjusting shaft 118 in that direction such as will move the pivot arm 98 rearwardly. The desired rearward position of arm 98 can be determined by visual observation of the pointer associated with hand wheel 134. When pressure fluid is alternately supplied to the power cylinders, starting with power cylinder 90, it will be seen that piston 94 thereof will be forced in a direction to the right to cause clockwise oscillation of the shear mechanism to an approximately 15 degree displaced position. Piston 95 of power cylinder 91 is forced into contact with the rear end of its cylinder 93 and in fact the contacting surfaces of piston and cylinder are so constructed as to trap a small quantity of pressure fluid in the rear of cylinder 93 to act as a cushion whereby to cushion the stopping action of the shear mechanism in said 15 degree displaced position. Following a cutting operation, the pressure fluid is now supplied to power cylinder 91, with the result that piston 95 is forced in a direction to the right. The shear mechanism will be oscillated counterclockwise into a displaced position approximately 15 degrees on the opposite side of the transverse center. Such oscillating action of the shear mechanism may be employed to cut a trapezoidal blank or a triangular blank. The stopping action of the shear mechanism is also cushioned in this counterclockwise direction since as piston 94 approaches the rear end of its cylinder 92 a small quantity of pressure fluid is trapped between the contacting surfaces and the impact and jar which would otherwise take place in bringing the shear mechanism to a stop is effectively eliminated.

A still further adjusted position of the parts is possible in order to provide for degree oscillating movement of the shear mechanism on respective sides of the transverse center. The pivot arms 98 and 100 are located in the position as shown in Figure 6 by actuation of hand wheels 134 and 135, which effect rotation of the adjusting shafts 118 and 119. The position of the pivot arms is such as to withdraw the cylinders of the hydraulic power means the maximum extent with respect to their pistons. Also, it will be observed in Figure 6 that the position of the pivot arms 98 and 100 is such as to effect pivotal movement of the adjusting shafts 118 and 119 around their respective axis 124 or 125. Although said adjusting shafts may pivot as described in order to permit a full range of adjustment as regards the pivot arms, nevertheless the geared arrangement between pinion 131 and its respective gear wheel remains intact. The universal joint 130 has location in vertical alignment with its pivot pin either 124 or 125, as obviously must be the case in order to make an operative structure. Upon oscillation of the shear mechanism with the adjustment of Figure 6 the mechanism will produce metal blanks 26 of the trapezoidal shape as shown in Figure 8 or of the triangular shape 42, as shown in said figure.

By rotation of the hand wheels to rotate the adjusting shafts 118 and 119, respectively, the pivot arms 98 and 100 can be infinitely adjusted within their range of movement to effect oscillation of the shear mechanism to a varying extent in either a clockwise or counterclockwise direction. By adjusting the position of the pivot arms the cylinder portions 92 and 93 of the power cylinders 90 and 91, respectively, are similarly adjusted with respect to their piston members 94 and 95. Thus the stroke of the piston member is varied and as a result the desired variation is secured in the degree of oscillation imparted to the shear mechanism. Certain adjusted positions of the pivot arms can be effected by the operator for producing the trapezoidal blanks such as 32, or for producing the triangular blank such as 43. In addition to oscillating the shear mechanism it is possible to lock this mechanism in any oscillated position within the range of the machine. As explained in connection with Figure 3, the cylinder portion of the power cylinders are both caused to contact their piston members so that the mechanism is locked and movement is prevented. Assuming the mechanism to be locked in a 15 degree clockwise oscillated position, it would thus be possible to produce the parallelogram shaped blank such as 33, a feeting operation on the strip material of predetermined length taking place between actuations of the cuttin knives to produce the cut edges and 41. Other locked positions of the shear mechanism may be resorted to for producing blanks either parallelogram, square or rectangular in shape.

The hydraulic cylinders 90 and 91 are alternately operated by supplying thereto a pressure fluid which, by acting on a piston member, will move the piston member in a direction outwardly of its cylinder member to effect the oscillating movement as described. Figures 10 and 11 disclose a preferred hydraulic system for operating the power cylinders. Referring first of all to Figure 10, it will be seen that power cylinder 91 is under pressure, having just been operated to move the piston member 95 thereof in a direction toward the left, that is, outwardly of its cylinder portion 93. As a result the cross arm 82 has been oscillated in a counterclockwise direction and piston member 94 has been moved in a direction toward the right to effect substantial contact of the member wlth the rear end of its cylinder portion 92.

The system essentially consists of a reservoir 142 and which contains oil or other fluid to be placed under pressure by the fluid pump 143 driven by the electric motor 144. The pipe 145 leads from the motor to a pressure relief valve 146 having connection with the reservoir. Pipe 147 connects the fluid pump with the main operating valve, generally identified by numeral 148, suitably fixed to the control panel 150 and being actuated into one operative position by the hydraulic member 151 and into its other operative position by hydraulic member 152. An auxiliary valve 153 is also located on control panel 150 and said valve is solenoid actuated by the solenoids 154 and 155, respectively. When solenoid 154 is energized the hydraulic member 151 is rendered operative and the high pressure pipe 147 is connected to pipe 156 lead ing to cylinder portion 93 of the power cylinder 91. The said power cylinder 91 is thus rendered operative to effect oscillation of the shear mechanism. The pressure fluid from cylinder portion 92 of the power cylinder 90 is discharged through pipe 157, through the main operating valve 148 to pipe 158, and eventually to pipe 160 having connection with the reservoir. Should any pressure fluid leak past the piston members during hydraulic operation thereof the fluid will be periodically discharged from cylinder member 92 through the flexible connecting pipe 161 and said fluid together with any from cylinder member 93 will be similarly discharged in a periodic manner through pipe 162, which returns the fluid to the reservoir.

When solenoid is energized the solenoid 154 is simultaneously deenergized. As shown in Figure 11, the hydraulic member 152 is thus actuated to position the main operating valve so as to connect the high pressure pipe 147 with pipe 157 so that the high pressure fluid from the pump is supplied to cylinder member 92 of the pressure cylinder 90. The piston member of the same is driven to the left, effecting oscillation of the cross arm and movement of piston 95 to the right. Pipe 156 now becomes a venting pipe, permitting flow of the fluid from cylinder portion 93 through the main operating valve 148 to pipe 158, which eventually delivers the same through pipe to the reservoir. Accordingly, by alternate energization of solenoids 154 and 155 pressure fluid is first delivered to power cylinder 91 and then to power cylinder 90 and each cylinder following an operation is automatically connected to discharge, so that the fluid can be returned to the reservoir.

In addition to employing the hydraulic fluid for operating the power cylinders, use is additionally made of the fluid to effect a cushioned stop of the shear mechanism in both a clockwise and counterclockwise direction. It will be appreciated that considerable power is required to start oscillating movement of the various parts since they are heavy and with the parts at rest static friction must be overcome. However, after the parts have been placed in motion they tend to accelerate and gain momentum, and it is especially desirable to cushion the moving parts prior to stopping their oscillating movement, The stop position of the shear mechanism is determined by the piston members 94 and 95 which come into substantial contact with the rear end of their respective cylinder portions. In order to cushion the impact which would otherwise occur should the two metal surfaces be permitted to contact each other, the power cylinders of the present invention have a unique construction, the same consisting of a tapered nose portion or projection 163 formed on each piston member and a recess such as 164 provided in the rear wall of each cylinder portion and similiarly tapered for receiving the projection of its respective piston member. Pipes 156 and 157 of the power cylinders communicate with the interior of the cylinder portions through said recesses 164. Accordingly, as each piston member is caused to move toward the end of its cylinder portion its tapered projection will first of all enter recess 164 in the rear wall thereof. This functions to cut off furtherdischarge of the fluid from the cylinder and the parts are so constructed and arranged that a small quantity of fluid will accordingly be trapped between the piston member and the rear wall of its cylinder portion. Said fluid functions to prevent further closing movement of the piston member since the same can only take place to an extent as permitted by the compressibility of the trapped fluid. Oscillating movement of the shear mechanism is accordingly cushioned prior to coming to a stop and the impact between the metal parts which would otherwise take place is eliminated in addition to alleviating the excessive stresses and strains such as would otherwise develop in the parts.

The invention is not to be limited to or by details of construction of the particular embodiment thereof illustrated by the drawings as various other forms of the device will of course be apparent to those skilled in the art without departing from the spirit of the invention or the scope of the claims.

What is claimed is:

1. In oscillating shear mechanism, the combination of a frame providing cutting knives for cutting metal strip material, of means including a base for supporting the frame for rotation about a vertical axis located centrally of the frame, a cross arm forming part of the frame and extending on respective sides of the vertical axis, a pair of pivot arms supported by the base for independent pivotal movement, hydraulic power cylinders interposed respectively between and operatively connecting each pivot arm with the cross arm so that operation of one power cylinder will oscillate the cross arm and the frame in a clockwise direction and operation of the other power cylin der will oscillate the said parts in a counter-clockwise direction, means adapted to be manually actuated for adjusting the position of the pivot arms respectively whereby to vary the extent of movement effected by each power cylinder upon operation thereof, and an hydraulic system providing pressure fluid for operating said power cylinders.

2. In oscillating shear mechanism, the combination of a frame providing cutting knives for cutting metal strip material, of means including a base for supporting the frame for rotation about a vertical axis located centrally of the frame, a cross arm forming part of the frame and extending on respective sides of the vertical axis, a pair of pivot arms supported 'bythe base for independent pivotal movement, hydraulic power cylinders for effecting oscillating movement of the rotatably supported frame, a power cylinder being disposed between each pivot arm and its respective extension of the cross arm with the cylinder member thereof having pivotal connection with a pivot arm whereas the piston member thereof is pivotally connected to the cross arm, whereby operation of one power cylinder will oscillate the cross arm and the frame in a clockwise direction and operation of the other power cylinder will oscillate the said parts in a counterclockwise direction, means adapted to be manually actuated for adjusting the position of the pivot arms respectively whereby to vary the extent of oscillating movement effected by each power cylinder upon operation thereof, and an hydraulic system providing pressure fluid for operating said power cylinders.

3. In oscillating shear mechanism, the combination of a frame providing cutting knives for cutting metal strip material in transverse directions, of means including a base for supporting the frame for rotation about a vertical axis located approximately centrally of the frame and disposed in substantially vertical alignment with the cutting knives, a cross arm fixed to the frame and extending on respective sides of the vertical axis, a pair of pivot arms supported by the base for independent pivotal movement, hydraulic power cylinders for effecting oscillating movement of the rotatably supported frame in clockwise and counterclockwise directions about said vertical axis, a power cylinder being disposed between each pivot arm and its respective extension of the cross arm with the cylinder member thereof having a pivotal connection with a pivot arm whereas the piston member thereof is pivotally connected to the cross arm, whereby operation of the power cylinders in an alternate manner will oscillate the cross arm and thus the frame in clockwise and counterclockwise directions, adjusting shafts adapted to be manually rotated and having operative connection respectively with the pivot arms for adjusting the position of said arms and thus the cylinder member thereof with respect to its piston member, whereby to vary the extent of oscillating movement effected by each power cylinder upon operation thereof, and an hydraulic system providing pressure fluid for operating said power cylinders.

4. Oscillating shear mechanism as defined by claim 3 additionally including hand wheels journalled by said base for effecting said rotation of the adjusting shafts respectively, a connection including a universal joint interposed between each hand wheel and its adjusting shaft, and wherein each pivot arm includes a cylinder nut having threaded connection with an adjusting shaft.

5. In apparatus for cutting metal blanks of various shapes from strip material intermittently fed thereto, the combination including oscillating shear mechanism having'cutting means for cutting said strip material transversely thereof while the strip is at rest between feeding operations, said oscillating shear mechanism including a base supporting a frame for rotation about a vertical axis located approximately centrally of the frame, power devices located on respective sides of the vertical axis and each including a cylinder having a piston adapted to reciprocate relatively with respect to the cylinder, each cylinder and piston combination being disposed between the base and the frame and being respectively secured thereto, whereby operation of one power device will oscillate the frame in one direction and operation of the other power device will oscillate the frame in a reverse direction, and an hydraulic system providing pressure fluid for operating said power devices.

6. In apparatus for cutting metal blanks of various shapes from strip material intermittently fed thereto, the combination including oscillating shear mechanism having cutting means for cutting said strip material transversely thereof while the strip is at rest between feeding operations, said oscillating shear mechanism including a base, a frame supported by the base for rotation about a vertical axis located approximately centrally of the frame, power devices located on respective sides of the vertical axis for oscillating the frame, each power device including a cylinder and a piston, and each power device being disposed between the base and the frame and being respectively connected thereto, the connection between each power device and the base being adjustable for respectively varying the relative positions of the pistons with respect to their cylinders for any particular oscillated position of the frame, whereby the extent of oscillating movement of the frame as effected by each power device can be varied, and adjusting shafts journalled by the base and adapted to be manually rotated for respectively adjusting the said connections between the power devices and the base.

7. Apparatus for cutting metal blanks of various shapes from strip material as defined by claim 6, additionally including hand wheels journalled by the base for effecting said rotation of the adjusting shafts, and means including a universal joint disposed between each hand wheel and its adjusting shaft.

8. In apparatus for cutting metal blanks of various shapes from strip material, the combination with mechanism for intermittently feeding strip material, of oscillating shear mechanism having cutting means for cutting the strip transversely thereof while the strip is at rest 11 between feeding operations, said oscillating shear mechanism including a base, a frame supported by the base for rotation about a vertical axis located approximately centrally of the frame, a cross arm forming part of the frame and disposed so as to extend on respective sides of the vertical axis, a pair of connecting members supported by the base for independent movement, hydraulic power cylinders for effecting oscillating movement of the frame, a power cylinder being disposed between each connecting member and its respective extension of the cross arm with the cylinder member thereof having securement at its rear with a connecting member whereas the piston member thereof is pivotally connected to the cross arm whereby operation of one power cylinder will oscillate the cross arm and thus the frame in a clockwise direction and operation of the other power cylinder will oscillate said parts in a counterclockwise direction, means for efiecting movement of each connecting member for varying the relative positioning of the cylinder member secured thereto so as to vary the extent of oscillating movemeut effected by each power cylinder upon actuation thereof, and an hydraulic system providing pressure fluid for operating said power cylinders.

References Cited in the file of this patent UNITED STATES PATENTS 524,501 Kendall Aug. 14, 1894 640,519 Ahlen Jan. 2, 1900 1,054,617 Regamey Feb. 25, 1913 1,984,717 Williams Dec. 18, 1934 2,269,714 Fcnton Jan. 13, 1942 

